Feed water heater for locomotives, etc.



y 1935- E. H. BLUNT FEED WATER HEATER FOR LOCOMOTIVES, ETC

Origifial Filed Oct. 2'7,v 1928 ll Sheets-Sheet. l

May 7, 1935. E H, BLUNT 2,000;009

FEED WATER HEATER FOR LOCOMOTIVES, ETC

Original Filed Oct. 27, 1928 ll Sheets-Sheet 2 .LLllILLEJ!!! awvawcoz May 7, 1935. E. H. BLUNT FEED WATER HEATER FOR LOCOMOTIVES,

ETC

Original Filed Oct 27, 1928 ll Sheets-Sheet 5 gvwemtoz Zuni,

y 1935- E. H. BLUNT FEED WATER HEATER FOR LOCOMOTIVES, ETC

l1 Sheets-Sheet 4 Original Filed Oct. 27, 1923 l I I I- y E. H. BLUNT zwww FEED WATER HEATER FOR LOCOMOTIVES, ETC

. Original Filed Oct. 2'7, 1928 .ll Sheets-Sheet 5 /MG L52 gave/mic:

y 1935- E. H. BLUNT 2,000,00

FEED WATERHEATER FOR LOCOMOTIVES, ETC

Original Filed Oct. 27, 1928 ll Sheets-Sheet 6 i Q .23? O imam filling 'zmwos May 7, 1935. E. H. BLUNT i FEED WATER HEATER FOR LOCOMOTIVES ETC , 1923 ll Sheets-Sheet 7 Original Filed Oct. 27

amvemtoz May 7, 1935.

E. H. BLUNT 2,000,009

FEED WATER HEATER FOR LOCOMOTIVES, ETC

Original Filed Oct. 27, 1928 ll Sheets-Sheet 8 M 7, 1935- E. H. BLUNT I 2,000,009

FEED WATERHEATER FOR LOCOMOTIVES, ETC

Original Filed Oct. 27, 1923 ll Sheets-Sheet 9 -JL 1 5 V a i- 2 29 May 7, 1935. E, H. BLUN-T 2,000,009

I FEED WATER HEATER FOR LOCOMOTIVES, ETC

Original Filed Oct. 257, 1928 ll Sheets-Sheet l0 May 7, 1935. E. H. BLUNT 2,000,009

FEED WATER HEATER FOR LOCOMOTIVES, ETC

Original Filed'Oct. 27, 1923 ll Sheets-Sheet 11 Patented M This invention relates particularly to'feed Water heating adapted to be the supply pumps and thefeedpumps deliver.

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PATE

FEED WATER HEATER ron-noooMo'rrvEs, Y ETC.- 3

Edmund H. Blunt, Brooklyn, N. Y.

Application October 27, 1928, Serial Renewed July-19, 1934 No. 315,579 F 16 Claims, (01. 122-442)v apparatus of the type specially used for locomotives, in which .to and remove from the heating vessel, approximately fixed q uantities of water, or in other words, where the ratio of incoming cold water and outgoing hot water remains substantially constant. Any normal should substantial variation from the be properlyneutralized by some water-levelcontrolled device.

An important feature of locomotive installation is to keep the vertical-dimension of the apparatus as small as.

sitates its being nism and below man.

In an install supplying cold water feed pump for waterand deliv the boiler, I pro acting supply pump and acting feed pump, assembled side by side and above the driving-wheel mechathe line of vision of the engine ation operated by individual steam: driven cylinders.

While the hot der a boiler pre more, the cold ssure of say 200# water per-sq. inch or pump may only have to overcome a resistance of 20 or 30# per sq. inch water into the heating vessel.

I propose to provide a system in which these different delive by the same boiler ring pressures can be produced pressure in the two steam cylinders by the simple expedient of making the steam cylinder the hot water in steam consumption.

of the pump which supplies pump.

The type of heater herein shown is generally known as an open which or contact heater, in

will alter this balance.

To rectify this, I have designed a float controlled by-pa-ss excess water fro of novel construction to transfer m one end of a pump to the other is practicable, as the at-.- 'taching of same to the side of 'the boiler neceswater pump should operate unthan the steam cylinder of This results in economyinstead of allowing it to be first discharged into' the vessel- This feature may be applied to either hot water pump or to-cold water pump, or to both pumps as will .be shown.

The entering cold water passes through a spray I head that may have adjustable frictional resistances therein. A secondaryjspray may be used whose function is that of maintaininga steady spray of water into the heater vessel when the supply pump has momentarily; stopped.-

These adjustable resistances in the cold'water. delivery may be. used tov control the speed of the cold water pump. I have also shown a resist ance introduced into the .hot water delivery that may be used to govern the speed of the hot water. Pump. ,1

-To externally condense excess quantities of exhaust steamand carry awaymost of the contained air that would otherwise remain in the vessel, I have provided aniaircooled condenser preferablysituated above the heating vessel and motive tender, and will water saved. J L

When using 'ahighpressure pump to supply the boiler feed and a low pressure, or'low duty pump as a means of cold water supply, there may be a decided advantage in compounding ;the steam fromone cylinder into'the other. the outline of-the adjoining steam cylinders is favorable to the formationof a, very-compact steam jacket about the cylinders;

To readily remove pump ends and make necessary repairs without that can be readily vessel. I

To prevent thehot water pump from losing its heat by. radiation, with aconsequent cooling of its contents, I have designed what I will term as an internal steam jacket,

plied by excess exhaust operated from without the steam from the heating vessel. It may bereg'arded as .internal when.

preferably supreturning said drainage compared to the usual type of eXt'ernaP jacket that would be placed outside thecylindfer.

A combination cold water bypass valve and a 'hot water bypass valve, both operated by a com'-' Val that will retard the speed whenever this pump requires slowing down. A mechanical Substitute for the usual air-chamber to reduce shock on the water lines, is also shown. 1

- Referring to the drawings- Fig. 1 is a section and elevatierithe heater on the general plane of the line E- -l of Fig. 6.

Fig. 2 is a top plan of the Fig. 1. I

Fig. 3 is a sectional plan view taken; onthe' line 3-3 of Fig- I. i

parts shown in' Fig. 4 is a sectional: plan taken entire line. 4-4 i of. Fig. 1.

Fig. 5 is "a; sectional plan taken on 5-5 of Fig.1. and 015 Fig. 33; i I

Fig. 6 is a front: elevation: and section taken on. the line, (L 6 01 Fig; 1; I

Fig. '7 is a. rear end elevation and; section. taken on the line,. II-1 of Fig; 1"

Fig. 8 is a plan section-thru the pumps on the line; 8--8 oi:Fig. 1. H

Fig. 91s a front end eIevationiontheline, 9 -5 Fig. 10 is a part side elevation of Fig. 9. r

Fig. 11. is a part sectional plan or the heater vessel and showing secondary spraypiping con-- nections. 1

resistance valve for the hot water discharge pipe, as assembled Fig. 33 1 Fig. 16 is an: elevationand:v section. showingthe float controlled. special valves within. the vessel.

Fig; 1'7 is av plan and section: of the parts of Fig. 16 taken on the line; u n of Fig; 16'.

'Fig'. 18*. is a; sectional-elevation on the: line I8-l8 0f Fi .1'7. 1

Fig.19 is as plan and section'takerr on the line 19--I9 of Fig. 16;. I

Fig; 20- is a detail or the noat valves or Fig. 16-" while the float is in its low position.

Fig. 21: is a detaii oi. the same with. the float lever in: its level or horizontal position. Fig. 22 is a. detail. 01 the same with-the float in its high. position; 1. Fig.v 23 shows a. changerin; the relative positions of the'uprp'er and lower valve. cams while the lever arm remains: 21.v

' Fig. 24:is a. section: and. elevation showing details. of the valvesirr'Figi'20 takenom'the' line 26-24- of Fig; 20.

Fig. 25 isa part section 'detail of aioot valve leading tothe air chamber of the secondary spray-head system.

Fig. 26 is a sectional detail of a balanced exhaust steam adrnissiorrvalve connecting the auxiliary exhaust steam supply with the heater vessel.

Fig. 27 is a side view of a locomotive'ieedwater heater, in connection with an air cooled condenser.

Fig. 28' is a rear elevation oithe. same onthe line 23-43 of Fig. 27'. 4

cylinder on line 7 v the line 48-48. of. Fig. Figs-12,13; l4; and. 15, are. detail sectionsof a 7 respectively of. the

19- are top and: bottomdischarge valves for the same, delivering the water thru conduit H: to

e by which it is jetted ing cold water from Fig. 29 is a similar front elevation looking towards the cab on the line 29-49 of Fig. 27.

Fig. 30 is a top view of the air condenser on the line 30-33 of Fig. 28.

Fig. 31 is a'section plan of the condenser on the line 3|-3| of Fig. 28.

Fig. 32 is a top plan of Fig. 33.

Fig. 33 is a side elevation of. the pump and heater, as adapted. to steam compounding.

Fig. 34 is an end view of details including steam piping on the line 34-44 of Fig. 33.

Fig. 35 is a plan and section of the compoundingsteam valve as assembled on the cylinder. Fig. 36 is a plan showing steam ports in the cylinder headwhen the valve is removed.

Fig. 3'7 is a vertical section of part of the steam 31-31 of Fig. 36. I Fig. 38 is a vertical section of the upper part of the cylinder on the line 38-38 of Fig. 35.

Fig. 39 is a plan view and section of a comthe heater vessel.

Fig.1. 40=is a vertical: section of the secondary" spray-head onlline 411-4 0 of: Fig. 39.

Fig. 451v is. a vertical section of the spray-head on the line bI- -M of Fig. 39. Y

42,43 and 4e are sections of the. spray-- head taken. on the line 42-42 of Fig.- 39;. showing; three positions of theinside resistances.

"Fig; 45' is a; part sectional elevation of. ad joining pumps and shows" an inner pump lining forming: part of an interior steam jacket.

Fig. 46- i's-a section or the: pump barrel taken: on the line 48 -48 of Fig. 45, but with the in terior lining removed.

Fig. 4:? isa-horizontal section thru the pumps and shows an: annular. steam heating space.

Fig. 48 is a fragmentary vertical section on t 4.7 and shows a double flange at thezbottom as part of the pump lining. Fig.4!) shows a mechanical substitute for the usual type of air chamber, as attached to the inlet of thewater. supply pump.

Fig. 50 is an alternative design of a. substitute ior-Fig. 4:9.

Fig. 5=l= is amechanical surge chamber on the dischar'ge lineoftheboilerfeed pump.

-The--hotwater feed pump is I and has a steam cylinder 2 fisee Fig. 1 et al.). The cold water supply pump 3-, has a steam cylinder 4. 5- is the main-portion of the attached heating. vessel, with a rear extension 6 and-a lateral addition 1,. while I is an exhaust steam supply conduit connected. with said vessel.

3 i-s-the cold water: connection: to the: pump,v 9 and.- 9 are-inlet valves for top and'bottomends cold water pump-While l 0 and thehollow attachment ll on the vessel body 5, and through l 3-to the primary spray-head 14-, into the steam filled space of the heater vessel, there becoming heated, and collecting in the bottom of said vessel.

This coldw-ater delivery tothe spray-head may under certain conditions become intermittent, aswillbelatershown, and will not always condense the steam in a uniform manner. To remedy' this,.I propose leading some of the incomthe bottom of conduit l-2 into alower conduit l5, through the special valve.-

l6 and store it temporarily in a secondary airchamber l1, (Fig. 9').

At the end of the pumping stroke the pressure will .fall in l 5' and an unbalanced valve l=6 (shown.

and opens intoin detail on Fig. 25 closes I conduit wallowing the contained water of I1 to flow into the secondary spray-head l9 (see Figs. 3 and. 39), so that when water ceases flowing through the orifices, 258 of the prim'arysprayhead I i, a further supply goes through i8 to the secondary head is until a new stroke of the pump puts pressure again on the'valve in i6 and closes the entrance to E8.

To shut oh? the contained water of the heater vessel during repairs, I propose using an interior valve normally clear of the hot water outlet, but adapted to be closed and alsoheld to its seat by the pressure of the water behind it. I

This valve 20, shown as open in Figs. 4 and 9, and in a closed position in Fig. 5, is preferably operated from without, suchas by revolving a shaft 19 carryinga pin 2ii' and travelling in a spiral slot in a hollow cylinder attached to -20. on being revolved will cause valve 20 to be properly seated. Valve 20 opens into hot water conduit 21, leading to the suction valves 22 and 22' of the top and bottom ends of the hot water pump I. I a I The hot water discharge valves 23 and 23 from the top and bottom of pump I connect with conduit 24 leading to the boiler la. Attached to 24 by a fitting 25 is the main air-chamber 25'. The strokes of the hot and cold water pumps are to be synchronized and the ratio of cold water and hot water volumes maintained in a manner to be later" described. I

In the conduit 24 and preferably adjacent to air chamber 25, I propose inserting an automatic resistance device to the flow of hot water, as shown in Figs. 5, 33 and others, which will be described later. I

Live steam for operating the pumps may enter as at 26, (Fig. 1), and go by a passage (not shovm) to a steam operated'main valve 27; which may be controlled by a tappet rod such as 28 in a well known manner, the exhaust steam passing into the conduit 21', through special valve 28 into vessel 1 or into pipe 2?, adjustable valve 29, conduit 29', and thence to waste or otherwise, according to pressurecondition's within the heater vessel.

In Fig. l is shown the piston 30 of the large steam cylinder 2, and rod 3| connected to the hot pumping piston 132, also the smaller steam piston 33 with rod 34 connected with the cold pumping piston 35. Steam passages 36 and 31 distribute the live steam from valve 27 to opposite ends of cylinder 2. 1

To simplify pump synchronization; I propose using a single steam valve 27 to deliver live steam to both steam cylinders. The uppersteam port or conduit 39 and lower port or conduit 4!! respectively, connect the top and bottom ends of the large and small cylinders and tend to cause a simultaneous starting of both pumps. If preferable, the upper end of one cylinder can be ported to the lower end of the other, and vice versa, the simultaneous but the-pumping strokes being in opposite directions. It'will be observed thatthe travel of the larger piston governs the pumping cycle.

To make sure the cold water pumping piston delivers its proper amount of water to the heater and so maintains the predetermined hot and cold water ratio, I propose toestablish a slightly greater piston speed for the cold pump. This may be accomplished by using a proper areafor piston 33, with an adjustable cold water delivery restriction in the spray-head, as shown in Figs. 30 to 44. q

r 42 has a counter weight t2 starting still occurring the pump remains at rest until reversed. 'As' this comes negligible.

To prevent an excessiveriseabove the normal water level within the heatervessel, I have-em ployed the principle of the pump operated, EX-g cess cold water bypass valve shown in myU. S. Y Patent #1,551,727, dated Sept. 1, 19.25, as here... illustrated in Figs. 16 to 24 of thisapplication; is used to prevent excessive:, lowering of said water level by the use of a hot shown .;and described; waterbypass. T

Starting withFig. 16, 41 is apartly immersed fv float valve in its low water position while,4'l'

The float leverand is supported by,

A similar means water bypass valve to be along with the above cold indicates the highwater stage.

shaft 43, on which is also mounted acam, eccentric, wedge or other device varied vertical travel of the body 41.

conduit 69 connects the top side of 46 lower end of-said pump. The opening of valve 46 allows cold water to pass fromthe bottom to pump (see Figs. 5, 16

the top of the cold water to 19).

Referring to Figs. -20 to 24, cam 44 is shown with a curved continues to be developed comes approximately horizontal, as shown in Fig;

21, the valve stem is kept at a radius distance I from the shaft #5 and cannot progress downward or the valve 46 leave itsseat. On a further travel upward of the float, the point 50 is passed by said stem extension, and thenearer it approaches the point 5!, the greater becomes itstravel towards 43; being on thearc of a shorter radius 50-(-Fig.

22) The interval between low and high float positions. cam 48, the pump pulsations; gravity, aspring seating device (not shown) orother means can come into action to operate the valve.

A similar control of extreme lowwater conditions may likewise be installed. Owing to'some:

accidental disturbance of the'hot and cold water ratios, a low water level might not have suflicient hydraulic head to quickly fill the hot water pump,

but would leave a space in front of the'reversed. stroke of the pump and a disasterous water ham-J mer might result from thiscondition. By autowhat I elect to term the through a similarly-pumpoperated bypass'valve, such as 58, a less proportion of hot water will be permanently lost to the heater vessel, and. the waterlevel will'be-the more matically returning deficit hot water,

easily maintained.

Instead of returning it directly to the vessel I propose passing: a' varying cold water system;

At the end of each stroke,.a water cushioning. device as shown in Fig. 45, comes into action and:

M, that permits a stem of the cold"-' water bypass valve 46, contained within the valvethe eccentric .01

perimeter, whose center coincides with that of the shaft 143 and until a point :,is reached, beyond which the curveis reducedtoa" An adjustable extension-45 of the stem iemay be used tokeep-it in the. arrows at 53 shows, the maximum openingoi the valve between the t As 45' is free from amount back to the" opposite end of theh'ot water pump as the water level changes, in a similar manner to that of the" j hot watenbypass valvea. 55 is a. vertically adjustable end of. the valve: stem. 56 and passes through. stufllngl boxfili and connects with valve 58 that may register on the; valve seat 58, Fig. Hot. water valve body 59 has a lower passage 60 that connects withzthe top of pump I, while the upper passage 6.1? communicates with the lower end of pumpl- (Figs. 4, 1 6, 18 and 19) Y InFig. 22=showing-the high position of the float,

it will be Seenthat the valve stem extension 55 'cannottravel towards the shaft; while in the low position shown in Fig. 20, the vertical valve play is the intervalfii betweenthelines. The positionofoneor both-cams 44 and. 54 may be shifted or rotated on the shaft 43', with respect to the float,

as in Fig. 23, thereby changing the time at which the valves commence functioning and by this means establishing a new average water level the heater vessel. 7

23 where the position of the float is similar to-that of Fig. 21, cam 44 has been rotatedto 'the rig'h-t and a gap 63 has developed, thereby opening up valve 45 while itstill remains closed in Fig. 21. On the contrary, a reverse movement of M te-the left (not shown) would delay the valve opening until point came under 45, the gen eral effect being to raise the average water level.

external tell tale 64 fastened to the shaft 43 and preferably contained in a box with a transparent cover 65' maybe used to indicate the position of float 4|.

It 'will' be readily seen that the bypass valves 46- and 58 are operated by the pump pulsations,

but" only when the float has rotated the cams keep valve ll'H sufficiently to open up at the gaps 53 and 82 for the'respecti-ve pumps; also that the float has merely to exert itself between pulsations, when most- 0f the pressure is removed from the valves. By this system all float failures due to corrosion or to tight connections may be eliminated, as slight valve stemleaks would remain within the ves'seF and little if any packing of said stem would be required, thus reducing friction to a' minimum. Positive and reliable float action. is

I thereby assured- Gn'Fig; 25 the details. of the foot: valve is are shown; Its location is also given in Figs. 9, 10 and Iii-Excess cold water enters from 15, lifts the large disc valve 66 on its seat 61, until the smaller waive-68 (adjustably connected to 68 by'stem 69,)

seats itself against the edgeand closes the open- Thecol'd water passes thru 61 and H into air chamber; I], until a proper'pressure is established therein. When this pressure diminishes, due to the cold water pump completing its stroke, the unbalanced pressure of the air within l1, acting against the unequal areas oi the discs 66 and 68,

closes the: opening: at 61, and uncovering the opening HI; allows water to pass into l8 and thence-tothe secondary spray'head #9 (see Figs. 3, 9,16 and 39):.

In modern feed water heater practice, the use 015 a; steam. and air vent to the'atmosphere is de- ,sirable as a means for preventing the heater from becoming airbound, and the greater the amount of: vented steam, the greater will be the amount of escaping-air, resulting in a diminished pitting of the boiler tubes. 7 I V Figs.- 27 to; 29 and condenser se'ctionsFig. 30 and: 31 show the installation of a combined boiler feed apparatus and air-cooled condenser, as assembled ontheleitside of a; locomotive, in which is a part section of the locomotive boiler, 81

-its running board, 82 a feed pump, 83- the operating steamcylinder' (or cylinders) 84- the cold. water supply line to-pump 82-; while 85 is the feed; line to the boiler.

The heater vessel 86 has a supply conduit 81 for steam heat, a water conduit 88 from the" pump. Anexhau'ststeam outlet 89 with an adjustable or automatic relief valve 90, has an excess steam conduit 92 connecting to an air cooled condenser 9!, having interior condensing tubesor elements, 93that will pass the uncond'ensed steam and included air into an outlet 94- from the condenser, thru adjustable relief valve 95 and pipe 96 to the atmosphereor otherwise.

Cold air inlet 9'1 to the condenser.is-vpreferably' placed at the forward end totake advantage of the speed of thelocomotive. A flaring flange 91' may be employed to force a greater quantity of air against the steam elements 93 to give the maximum condensation. --The air outlet 98 from the condenser, is shown at the rear.

Steam condensation in the tubes 93 will fall to the enclosed bottom 93: and flow thru pipe 99- toa specialcontainer H10, that is designed to form a water seal against any reverse flow of steam or.

.so that, combined with the weight of valve and parts, it will be greater than any vessel pressure thatwould force thesteam back thru pipe roe.

Pipe lG3= should drain into 86 at some such point as HM, high enough to be readily reheated.

by the'steamwithin the heater vessel. It is desirable to: drain this condensate to' the feed pump systemwhen using'this type of condenser with aclosed or pressure heater.

By adapting this air cooled condenser a feed water system we will get rid of otherwise objectionable quantitiesof escaping steam that tend to cloud the enginemans' vision. At the sametime a saving in water consumption is assured bythis air condensation and a correspondingreduction in the amount of minerals formerly Y discharged into the boiler is secured. V

Instead of using live steam tooperate the small cylinder of the cold water pump as shown in Fig.

1, it might be advantageous to use a slightly larger cylinder, and compound the exhaust from the large cylinderinto it. 'To simplify matters a single steam valve could be used for both pumps, the travel of the larger hot pump piston governing the cycle, and the cold pump running at a greater speed, to be controlled as formerly described.

On Fig. 33 is shown a side elevation of such a design, while Fig. 32 shows a top plan of the same.

Identity numbers on pumps and heater remain substantially the same. The compounding valve body 258 is also shown in Figs. 35,, 36, 37 and 38.

Its interior has a cylindrical bushing 2M and has opposing steam ports 202'.

lhis steam operated. main valve 203, has a large piston 264 at the right end, a smaller piston 265, atthe left, with four cylindrical slides 286, that travel withand area part oi the valve, and cover and uncover the various ports 202, in a:

i enters at 23!,

well known manner. Slotted ports 201, 208, 209, 2 ID and .2! I, Fig. 36, lead respectively by passage 2! to the bottom of the high-pressure steam cylinder 2 and by passage 213, to the top of the low-pressure cylinder 4 and by passage 2M to steam-jacket receiver M7, and by passage 2:5 to the bottom. of cylinder 3, and by passage 2H3 to the top of cylinder 2.

Passage 2 I8 is an exhaust rear piping 2H9, with a check. valve 220 and a cross fitting 22 1, while passage 222 (Fig.35) is an exhaust connection to the front piping 223, with a check valve 224 (Fig. 32) and also connecting with cross fitting 2.2L From the bottom of 22L a conduit 225 with check valve 225 admits steam to the receiver 2", enclosed by jacket 2H.

From the top of cross 22!, piping .221 witha regulating valve .228, connects with special valve 28 (detailed in Fig. 26) and thence to the heater vessel or to the exhaust connection 29' and the atmosphere as shown in Figs. 1 and 2. A steam outlet 229 with interposed regulating valve 230, connects with 221 and can be used to prevent excessive pressure within the receiver. Live steam Figs. 3, 5 and 38, and by passages 232 and 233 to the respective inner faces of valve pistons 2M and 205.

- With the outer faces of pistons 204 and 205 at atmospheric pressure, the valve 263 will be to the right. Live steam from 233, passing through holes 202 will enter 201 and 2L2, causing the large steam piston of cylinder 2 to rise. Reduced pressure steam from receiver 2 I 1 will pass through 2! and slot 209 into slot 2H] and passage 215 to the bottom of the small piston, causing it also to rise. When the large piston rises sufficiently, it causes the tappet rod 234 to shift the auxiliary steam valve .235 in a well known manner, thereby admitting live steam pressure to the outer face of piston 204, by steam passages (not shown) and valve 200 will shift to the left, due to unbalanced steam pressure on piston 205.

High pressure exhaust from below will then pass out through H2, 23?, holes 202 into and through H9, 220, .22l, 225 and 226 to receiver 2|1, aswell as through the top of the cross 22I, 221, etc. to the atmosphere or otherwise, 'as described. A proper adjustment of valve 228 will regulate the steam flowing to the receiver and also the resulting pressure. Any excess pressure can be regulated by the valve 233. As soon asa pressure drop occurs in 2.21, any back flow from the receiver is stopped by check valve 225 and the steam is retained in the receiver at the required pressure. This charging of the receiver is ex--' tremely rapid and will not interfere with the secondary exhaust from the low pressure cylinder;

On the shifting to the left of the steam valve 283, the low pressure exhaust from belowwill enter M5, 210 and holes. to passage 222, piping 223 and valve .224, as soon as the momentary pressure drops sufficiently in 227, this exhaust then escaping to the atmosphere.

At the same time, live steam passes from passteam connection to sage 232 into 2! IV and passage 2m, to the top of the high pressure piston, forcing it downwards, while the low pressuresteam from receiver 2I1 flows through 214, 239, .208 and into passage 253 to the top of the piston of steam'cylinder 4, also forcing it downward. On reaching the lower end of its stroke,.the piston of cylinder 2 pulls'down the tappet 234 and the valve 235, thereby releasing live steam from the outer face of piston'204 ina well known manner and allowingthe unbalancedinternal steam pressure to return the .openings 252 tive numbers of these steam valve to the original positionas shown in Fig. 38; thus completing the cycle.

Fig. '26 is a detail of an'auxiliary exhaust steam admittance valve 28, as shown in Figs. 1, 2,32 and 33. Passage 239 connected to'pipe 21' of Fig. 1 may be regardedas the entering connection of anyauxiliary steam supply to this valve, and 240 is any connection by which the steam may normally escape to atmosphere by means of pipe 29. Also 2 connects with the heater vessel, while 242 is a valve seating on 243 and freely. travelling on and supported by stem 2 which is capable of. vertical adjustment, as by the thread 245 in the cap .246. An adjustable spring 241 is mounted'on 24 4 and tends to keep the valve normally 01f the seat, regulating the steam admission.

The valve should be light and of large area so that its vertical travelneed'be comparatively small and to open and close on slight-changes in the steam pressure. At steam pressures Within the heater vessel under normal operating conditions, the valve should be adjusted so that this pressure keeps it seated. When this vessel'pressure drops below a predetermined point the spring will cause the valve to lift'and admit a certain amount of auxiliary steam. It will be seen thatwhen only 'atmospheric pressure exists within'the vessel, the auxiliary steam may enter' without excess" pressure while at slightly higher heat pressures the valve will close.

The combined type of primary and secondary spray head and means forintroducing variable resistances in it are shown in Figs. 39 to 44, while its assembly with thesupply piping andadjoining float is shown'in Fig. 3. The primary spray head I 4 with discharge orifices 250, and 252 is supplied through l3 by the cold water pump 3. Before reaching 25] and 252,-the water flows through 'a hollow cylinder 253 within the spray body and capable of being rotated by external means such as a lever at 254 attached to shaft 254'. Said cylinder has peripheral ports such as 255, at times connecting with openings 25L also ports 256,'-discharging into openings 252, while at other times the rotation of 253 first'shuts ofi openings 25! while a further rotation closes the leaving only the openings 250 through which the water can be sprayed.

Fig. 22 shows both 25! and 252 being supplied with water. Fig. 43 shows a partly rotated cylinder which'supplies 252, while in Fig. 44 a further rotation cuts them both off. This device shows three stages of'resistance that give three different pump speeds, and can be used to regulate the travel of the cold feed pump whenever necessitated by the pump speed control demands.

The secondary spray,head I9 is here located between and above openings 25i and 252. Cold water coming from air chamberjil goes through I8 to passage 25'! and is forced through openings 258 into the heater'vesseh Changing the relaopenings, such as by the plugging of some and the opening of others, will give varying vresistances and corresponding changes of pump speeds. To maintain the-maximum pump speed, it is necessary that thehot water supply flows readily from the heaterto the hot pump, -as otherwise a disasterous water hammer may occur. As this apparatus is designed within minimum vertical dimensions, not much reliance. should be placed on thehydraulic head established, so I intend to. take advantage of'the high internal steam pressure of the vessel when operatingnear capacity. j I 1 However, any: sudden falling. off of said, pressure will have disasterous .results unless .the pump speed can be immediately reduced. .This reduction I propose to accomplish automatically. As one such wayI have shown automatic resistance introduced into the hot water pump discharge, this being especially necessary where the hot-pump speed governs the pumping cycle. Though three or more different pump speeds may be desirable, I have here shown but two. I propose to varythe. speed insome direct ratio to the pressure within-the heater vessel, such as by increasing the resistance tothehot pump discharge in an inverse ratio to the vessel pressure. But a device operated directly by slight variations of, pressure within saidvessel would not generally develope enough power .to over come the friction incurred in moving such a mecha: nism, such as I propose introducing into the high pressure conduit leading to the boiler.

Fig. 34 shows my proposed device in conjunction with a feed;water heater system, with a plan view in Fig. 3,and details inFigs. 12, 13, 14 and. 15. 3' 1 a Y A drop in heater pressure below .a predetermined limit is used to:admit live. or high pres sure stem to an unbalanced piston, iwhosetravel tends to revolve a disc or other obstruction across the path of the hot feed water, andsoincrease the resistance, as will be. shown. Above this pressure limit, the boiler feed pump may maintain its maximum speed, while any i drop below this limit causes livesteam to be brought into action, resulting in an immediate slowing down of the pump. p An upper valve body266 (see Figs. .12, 13, 14 and 33) is attached to a lower body .26 l through which hows the boiler feed from conduit 24. The body 260 contains an inner piston 262 with a larger upper head whose'outer, faceat times is exposed to boiler pressure-and the inner face to'approximate atmospheric pressure and is connected by a rod to a smaller diameter piston 262', the inner face of which is at nearly atmospheric pressure while its outer or lower face is in contact with the boiler feed flowing through 26I and thus subjected to that pressure.

An extension of this valve intothe body 261, preferably in the form of ;a stemiof square cross section to pass through a square guide and so keep the valve 262 from rotating, carried a disc 263 mounted on a hollow spindle 264 with a diagonal groove 264, in which travels, a pin 265, fastened to the square stem of valve 262 and capable of rotating said disc as the valve and pin travel up and down. f t

Adjacent to 266 is another valve body 266, containing a valve 261, having a stem 268 that may move the slide valve 269, but is kept in position by the adjustable spring 210 that may be regulated by rotating the exterior handle 21|.' Theouter face of valve 261 is subjected to the steampressure within the heater vessel .1 which is brought (see Fig. 33). Pipe 2 13 conveys live steam from the pump steam line to passage 216 invalve body 266. A drain 214, r naintains atmospheric pressure on inner faces of pistons 262 and 262. Set screw 215'regulates the travel of the double piston valve 262.

High steam pressure is maintained at all times in passage 216 by pipe 213. When the vessel pressure is above the critical point, itforces the valve 261 against the adjusted spring 210 and mainby the pipe 212 .tains the slide valve 269 operating over ports 216,

into the position shown in Fig. 12. While the top of 262 is substantially under the same vunit pressure as the bottom of 262 in contact with the water, (both being under. boilerpressure) the larger area of the upper piston is sufiicient to rotate disc 263 and keep it down in the-position as shown.

Under these conditions the disc 263 is kept parallel to the flow of water and a minimum resistance is encountered. Fig. 15 shows a sectionplan of body 261 with a disc infull lines whilev in its non-resistance position, and it also shows it ina dotted position as 263 whereit opposes the flow of water and builds up a resistance. 1 When the vessel pressure through 212 drops until it is unableto' oppose the spring 216, the valve 261 and slide valve 269 shift to the right, covering live steam port or passage 216 but allowing the steam in 260 to escape thru 211Land intoipassage 218 and to, the atmosphere. vThen the unbalanced pressure exerted on the lower piston. 262' by. the water pressure in the lower body 26l causes the valve pin 265 to rise, thereby rotating the disc 263 against the fiowof .water'irito the position 263. It is not necessary for this disc to entirely close the passage or to revolve ninety degrees. Experimenting will determine the amount of resistance required. A means for the interior steam jacketing of a hot water pump to prevent a temperature drop of its contents is shown in Figs. 45, 46, 47 and 48. As longas the steam. supply is in excess of the condensation, no appreciable internal loss of heat will occur... I propose using excess exhaust steam from the heater. to accomplish this, draining the resulting condensate away. i l Outside orexterior steam jacketing would require an outer containing shell and insulation to retain the heat, thus increasing the bulk of the pump, besides making it difficult to adapt to the outside irregularities of the apparatus. Bymy method, this inside jacketing can be carried up into the body of the casting, well beyond the limits otherwise imposed by the valve chambers werethe outside method of jacketing used. As theoutside body of thepump barrel would help retain the heat, only a thin outer insulation would be required with mydevice. 1 Fig. 45 shows two adjacent pumps, only the left one having been jacketed. No. 3| is the hot water piston rod operating through the combined stufling box and water cushion 3 l to move the pump piston 32. Let 286 be the lower head of the pump, 28! the pump cylinder lining with a bottom flange 282 bearing against or fitting into the pump barrel. Outlet holes 283 in this lining at its lower end allow passage of water to annular chamber 284 that communicates with the valve chamber above by passage 285.

Small openings 266 within the lower cup of piston 32, allow entrapped air to escape to 283 at the end of the stroke. On the completion of the downstroke the lower edge of the piston increasingly intercepts water flowing through ports 2B3 progressively brings the pump stroke to a stop, while at the end of the upstroke the upper edge of said piston intercepts water, that is passing out through 286 and the small holes 286 in theupper partof stuffing box 3|.

Fig.46 shows a section of the pump barrel with the lining 281 removed, also showing internal ribs 281 that, in conjunction with the removed lining 23l, form a number of narrow annular passages 288, to be heated by steam. For instance, exhaust steam is conveyed from the heating vessel 5, through non return valve 289 and pipe 290 to'a connecting passage 29! with holes 292 that permit steam to fill the passages 288; while other holes 293 drain the condensate from these annular passages to another connecting passage-294, then passing outside the pump barrel through regulating valve 295 from which it can run to waste. Y

These passages are arranged so-that the condensate does not block the flow of steam to any essential heating surface. A vertical rib 236 causes the steam to take the longest path between 29l and 294. Lining 291 of cold water used in common practice, shows the difierence between the two pump lining systems; A detachable cover 293 forms passage and a similar cover 299 forms passage 295. A modified cylinder lining is shown in Fig. 48 and is numbered 299', with a principal flange 353 bearing against an inner shoulder of the pump barrel, I b, preventing water from entering lower annular passage 288. A lower secondary flange 332,: loosely fitting said barrel, forms an annular passage 284 connected to the passage 285, that leads to the pump valves.

i Extra admission holes 303 in flange 362, a number of which may be opened or closed as required (such as by plugging), provide adjusting means for governing the cushioning at the end of the down stroke, such as by varying the totalarea of these discharge orifices and thereby altering the frictional resistances. In Fig. 48 the pressure in passage 284 tends to seat flange 353 against shoulders3fil and to tighten the joint.

Should. the temperature orfthe water within the pump lining reach 212 F. there could be no transfer of heat to without said lining, as the surrounding steam in the spaces288 would have at least the same temperature and there would normally be enough exhaust steam from the heater vessel to make up for any condensation that might occur by heat transmission through the comparatively thick metal of the pump casting lb, to the outer surface.

Interior arrows show the general flow of this exhaust steam around the inner lining, finally passing out to the atmosphere through valve 295, together with the. accumulated condensate.

To eliminate the possibility of waterhammer, .for instance, in the cold water suction line to the pump at the end of each suction stroke, due to the surge set up, I propose employing a substitute for the usual air chamber.

In Fig. 49 is shown portions of a feed water heatervessel, of a cold water-pump with suction or inlet valve, a discharge to the vessel, also a novel form of surge valve and an excess cold water bypass to said vessel. Interior arrows show the normal flow. I

The cold water supply conduit 8 to the pump 3 has a'surge valve chamber aw connected by pipe 3!! to a spray head 3l2 in the heater vessel 5 while 8a is the pump discharge to. 5. valve (H3 is pressed down by spring 3H1, adjusted by nut 3i5. A check valve 355 is placed in the line 3| I and the inlet valve 9a is located between the chamber 3m and the pump cylinder 3. Whenever a sudden closing of the valve 9a sets up asurge pressure in the line 8, the valve 3! 3 opens and allows the water to pass to the spray A movable head 3I2. When the surge ceases, the spring 3 M will close valve 313.

Fig. 50 shows a modification in that a piston 359. travelling within the-modified surge body 323, is opposed by the spring 32l, adjustably regulated by the nut 322. This piston is adjusted to rise and relieve the momentary impact from the sudden stopping of water again by the action of the spring in time toreceive the next stroke. This apparatus'may be made small and compact and will not take up the space usually required for an airchamber the air chamber. In my proposed mechanical substitute I intend arate the steam from piston such as shown in Fig. 51.

Let 5 be the heater vessel, 2| the hot water conduit to hot water pump I, 23 the hot water discharge valve, 24 the hot water conduit to the a special valve body inserted into Within the body is a water tight piston 324 whose lower surface is in touch with the water delivered to the boiler. It is connected to a-piston 325 by the common valve stem 326 that preferably extends without the valve body, as through the stuffing box 328. a v

The upper surface of valve 325 is in contact with and exposed to, the pressure of steam in chamber 32 5 delivered through pipe 330 and regan adjusting valve 330', this steam in the hot water conduitv 24. A steam bypass 33| and check valve33l' may be inserted, as shown.

The stem 326 above the valve 325 may have 'a removable sleeve 32? of varying diameters adapted to pass through stuffingbox 328 with like adjustments. While the surface areas of the top of 325 and the bottom of 324 when once established will remain fixed, the ratio may be altered by changing or substituting different diameters of sleeves until the proper ratio is determined that will returnthe piston 324 to its low position in time to receive the next pulsation of the pump l. 1 1 r Each pulsation should drive piston 324. .(andl consequently piston 325) against the elastic and compressible steam and thus cushion the blowin a similar manner to that of an airchamber. Drainage or relief means 332 and-333 above the valves325 and 324 may be provided, as shown.

When steam is supplied through pipe 330 and valve 335, said steam will be underincreasing compression during the rising of piston 325. With the addition of bypass 33! and check valve 33! an opening of valve 330" allows a momentary return of steam towards the boilerand said bypass may be used to further modify the travel of piston 335.

. .Frequent inspection isinecessary to determine whether enough air remains in an air chamber such-as, 25!;Fig. 1, to withstand and absorb the water hammer of each pump pulsation. Whenever theexisting type of air chamber fails it becomes necessary to shut down the feed pump, drain the pipe line to the boiler check valve, and then admit air tosaid chamber before starting up the pump again. All this will be avoided whenever my mechanical chamber is used in place of the other type. This surge chamber may be also employed in the secondary spray head system in place of chamber l1. Asa final means of automatic pump speed regulation I have shown (on Fig. 1) a governor 340, in the livesteam line 26 to the pump, and pressure pipe 34! from the heater vessel that may be adjusted so that a falling ofi of pressure in the steam heatingsupply to below that of a predetermined minimum, is immediately followed by a reduction of the live steam supply to the pump anda-consequent slowing of pump speed. This may be adapted to two or more successively slower stagesof speed, whenever the pressurelessens within the heatervessel. Racing or hammering of the high pressure hot water pump, due to its high speed when sufficient water is not passing through the hot water suction valves, is thereby avoided, j V 7 he general operation of this invention and its allied attachments'are as follows; .Coldsupply water from the locomotive tender enters the pump suction and is sprayed into the steam space of the heater vessel receiving heating steam from the locomotive exhaust. The spray head within the vessel is adapted to several different resistances to this incoming water. The vheatedwater and resulting condensate fall to the bottom of the vessel and are withdrawn by thchot water feed pump and forced to the locomotive boiler.

Both the cold and hot water pumps are double acting, i.-e.: each makes a delivery from alternate ends to a single discharge conduit and so supplies a. nearly constant fiow to the, boiler. Themomentary pause during reversal of each stroke is modified by the use of an air chamber, in-a well known manner.

.; To cushion the pumping pistons at the end of each stroke and so prevent possible violent impactagainst the cylinder heads, I have provided a means of decreasing the water discharge openings-as each piston nears the end of its travel. The normal water level within the'vessel as determined-by the steam space above it and the required hydraulic head for the hot suction water valves, is maintained as follows. Adoptingv the same number of strokes for each pump, a definite ratio is established between the volume of in coming coldwater and the removed hot water from the heater.

'.The steam condensate though, may vary from the zero, when no steam enters, to fifteen or more percent ofsame when at maximum condensation.

Should thepump volume ratios be such as to maintain a constant water level at zero condensation, then a water level float controlled means is employed to prevent injection water (to an amount equal to the condensate) from permanently entering the vessel, such being bypassed from endto end of thecold pump cylinder whenever to work. A 7

Another device is shown, wherein a hot water the float rises and allows thebypass deficit bypass, on the lowering of the water level float, permits a-fiow between opposite ends of the hot water pump cylinder, thereby preventing a permanent removal of thiswater from said heater vessel. adjustments of the float controlled bypass valves shown within the vessel.

A secondary water spray is shown that comes intoaction whenever a, temporary stopping of the cold supply pump ceases to feed the primary spray head, and thus maintains a continual condensation within the vessel.

A means for immediately and automatically slowing down the feed pumpspeed when the interior pressure of theheater vessel or its source of steam supply falls off, is set up in the pumps discharge conduit by which increased frictional resistance within, puts an extra load on the pump discharge with a consequent slacking of speed, whenever said, interior heater pressure drops below a predetermined point.

The cold water supplypump has a steam. cylinder that is smaller than that of the hot water feed pump and is preferably made, as small as is consistent with the speed required to normally keep it in advance of the latter. This willbe determined by the usual pump friction, to be encountered, plus a determinable resistance that may be encountered within the spray head; On reaching the end of each stroke the cold pump gradually comes to" a stop,.and 'is' not reversed until its companion pump is ready to change its own stroke. i p

A steam operated mai steam valve, reversed by the latter pumps. action,; supplies live steam to both steam cylinders, and both reverse their strokes at the same time. The pump exhaust passes to the atmosphere or to within the heater vessel, as required by the heater vessel pressure conditions.

Venting of excess steamto without the vessel in varying amounts, is accomplished thru a regulating valve that will also pass out a maximum of the air that should be removed from said vessel. The comparatively large amount of steam that should be allowed to escape is mostly condensed in an externally placed condenser, air cooled and located on'the top or upper side of the locomotive boiler, well above the heater vessel. The resulting condensation returns to said vessel, while a regulated amount of: the remaining steam and included air finally reaches the atmosphere and is dispersed.

Means to compel the steam to follow its prescribed course and not to flow out thru the condensate connection,out from the condenser are herein shown.

To retain the benefits of the usual air chamber as installed on most pumps but also to assure the greater reliability of not being subjected to the loss of the necessary air contained therein and its undesirable transfer to the locomotive boiler, a mechanical substitute for the same has been employed that is much preferable.

This uses the pressure of live steam as an elastic force when in conjunction with high duty pumpmg.

A means employed for low duty pumping allows a small quantity of water from time to time, to force back a valve,'that is returned to its first position at the end of each pump pulsation, such as by means of an adjustable spring.

It will be seen fromthe preceding pages that I have invented an extremely compact and emcient feedwater heater and pump outfit. its ver- This is illustratedin the regulations and one of several places on a modern locomotive.

2,000,009 tic'al dimension being kept at a minimum while I its other dimensions permit its installation on Automatic devices are also shown that relieve the enginemen from having to paymuch attention towards its operation.

Auxiliary steam heating supply and pump speed control, obviate the accidental pumping of cold water to the boilerwhile the air condensation of excess exhaust steam adds to the general economy. Adjustable throttling of the cold spray to the vessel allows a ready control of the cold pumps speed within narrow limits and simplifies the control of the main steam valve of the pump.

For instance to adjust and operate the pumps shown in Figs. 1, 2, etc. when theyhave the same unit live steam pressure Within both high and low duty steam cylinders, a small diameter steam piston is employed to reduce the total thrust developed in the low duty supply pump 3, keeping its piston speed substantially down to that of its companion high duty pump.

' To finally adjust its speed to the proper limits, adjustable resistance can be set up in the supply pumps discharge line, such as the perforated rotating hollow cylinder 253 within the spray head (shown in Fig. 39). r

With the maximum piston speed of the high duty pump l established, adjustments to 25$,may .be made that will normally keep the low duty piston speed slightly in excess of Proper cushioning of the smaller pump at the s end of each stroke will slowly bring it to a stand- :still and so be ready to reverse its travel when the high duty piston ends its stroke and shifts the main steam valve 21.

' Automatic slowing down of the high duty pump whenever there is not enough pressure within the heater vessel to force the proper amount of water through the suction valves and so maintain contact with the pumping piston at all times, insures additional safety of operation.

'The steam end of the piston in the pump line resistance may be made large enough to cause a flow of water towards the boiler check valve dur-- ing the pumps reversal of stroke, thereby preventing the seating of the valve and its consequent pounding. Again by preventing the ready escape of steam from above this piston, an excess pressure could be built up, that would accomplish similar results. j

The air cooler condenser for excess escaping steam vented out ofthe heater vessel, is not reystricted as to capacity. A small size apparatus located at any convenient place on the upper part of the locomotive boiler will condense an amount of steam determined by the exposed area of the :steam units and their contact with the cooling ,air. The employment of a large unit would handle more excess steam, all this to be existingconditions.

While the various improvements of this invention have been shown as partsof a general design determined by for an open type of feedwaterheater, some may be readily applied to a closed or heater also. I a

For example, this would include the automatic pressure type of v resistance within the pump discharge, an improved auxiliary steam supply valve, an interior steam jacket for the pump, an external airjcooled steam condenser and means for handling the con-' densate therefrom, and also a mechanical surge.

chamber placed in the pump lines. I

The term excess cold water is herein applied to that water or its equivalent that if permanently turn means.

the other pump.

. double discharge pump, in which a discharge occurs at each stroke of the pump, and into a common discharge conduit.-

The term low duty pump may properly be applied to the cold water pump which draws cold water from the supply tank and forces it into .the heater vessel at" a relatively low pressure and the term high duty pump maybe applied to the:

hot water pump which draws hot waterfrom the heater vessel and forces it into the boiler or other consumption means ata materially greater pressure.

I claim: a

1. In an open type feedwater heater, a steam heated vessel, cold waterv supply means and hot water removal means, an excess cold water return means, a deficit hot water return means, and

common water level control means for influencing the excess return means and the deficit re- 2. In a boiler feed system, including. a heater vessel supplied with heating steam, a-boiler'feed pump, a conduit connecting the. pump with the heater vessel and means for introducing resistances into the pump discharge conduit and causing a greater projected surface tobe opposed to the passage of delivery water whenever the vessels internal pressure diminishes below a predetermined point and vice-versa.

3. In anopen type feedwater heater, a steam heated vessel, a primary spray head, a second spray head, a water storage chamber connected to the secondary sprayhead, and means to cause Water to flow from said storage chamber to said secondary spray head when the primary spray head substantially ceases functioning.

said pressure substantially ceases, means causing water in said container to flow said secondary spray head.

5. Ina feedwater heater, a heating vessel, a main steam supply means for normally heating the same, auxiliary exhaust steam supplyv means connected both. to the vessel and to the atmosphere, said vessel connectionsincluding'an admission valve having adjustable means that keeps said valveopento the vesselwhen the pressure within the vessel is nearly'atmosphe'ric, while a greater increase in the vessel pressure'tends to close said valve. 1 i

6. .Ina feedwater heater,a heater vessel, a conduit leading to the heater vessel, a pump line and a pump drawing heater supply water through the pump line, a surge valve chamber connected to said pump line, said chamber being connected by a water conduit'tosaid vessel and'said chamber being provided with a spring pressed relief valve'that opens-with a predetermined excess water pressure in. said pump linepermitting waterlto pass by said'valveand to fiow through the conduit leading to the heater vessel.

7. Boiler feed water supply apparatus comprising a steam heated vessel, a double acting low to and thru 

